EP2525050A2 - Exhaust gas turbocharger - Google Patents
Exhaust gas turbocharger Download PDFInfo
- Publication number
- EP2525050A2 EP2525050A2 EP12160695A EP12160695A EP2525050A2 EP 2525050 A2 EP2525050 A2 EP 2525050A2 EP 12160695 A EP12160695 A EP 12160695A EP 12160695 A EP12160695 A EP 12160695A EP 2525050 A2 EP2525050 A2 EP 2525050A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- turbine
- nozzle
- housing
- inner housing
- turbine housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/243—Flange connections; Bolting arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/026—Scrolls for radial machines or engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2230/00—Manufacture
- F05D2230/50—Building or constructing in particular ways
- F05D2230/51—Building or constructing in particular ways in a modular way, e.g. using several identical or complementary parts or features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/30—Retaining components in desired mutual position
- F05D2260/36—Retaining components in desired mutual position by a form fit connection, e.g. by interlocking
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
Description
Die vorliegende Erfindung betrifft ein Turbinengehäuse eines Abgasturboladers, wobei das Turbinengehäuse ein Außengehäuse und ein Innengehäuse gemäß den Merkmalen im Oberbegriff von Patentanspruch 1 aufweist.The present invention relates to a turbine housing of an exhaust gas turbocharger, wherein the turbine housing has an outer housing and an inner housing according to the features in the preamble of patent claim 1.
Verbrennungskraftmaschinen, insbesondere im Einsatz für Kraftfahrzeuge, werden in zunehmendem Maße durch Strömungsmaschinen aufgeladen, um den Wirkungsgrad bei gleichbleibendem Hubraum zu verbessern. Hierdurch steht entweder mehr Leistung zur Verfügung oder aber es wird bei gleichbleibender Leistung weniger Kraftstoff und somit auch weniger CO2-Ausstoß produziert.Internal combustion engines, especially in use for motor vehicles, are increasingly being charged by turbomachines in order to improve the efficiency while maintaining the displacement. As a result, either more power is available or it is produced at constant power less fuel and thus less CO2 emissions.
Im Zuge der Motorenentwicklung wird eine Auflademaschine oder aber eine Strömungsmaschine, insbesondere ein Turbolader an die Leistungscharakteristik des jeweiligen Motors angepasst.In the course of engine development, a supercharging machine or a turbomachine, in particular a turbocharger, is adapted to the performance characteristics of the respective engine.
Damit der Turbolader selber mit einem hohen Wirkungsgrad arbeiten kann, ist die Einhaltung exakter Spaltmaße einzelner Bauteile des Turboladers vor, während und nach dem Betrieb von besonderer Bedeutung. Zwischen den einzelnen Betriebszuständen treten Temperaturunterschiede von bis zu mehreren 100°C auf, die bei den verschiedenen Bauteilen und bei eingesetzten Werkstoffen sowie Materialstärken voneinander abweichende Wärmeausdehnungen der Bauteile untereinander zur Folge haben.In order for the turbocharger itself to operate with high efficiency, the observance of exact gap dimensions of individual components of the turbocharger before, during and after operation is of particular importance. Temperature differences of up to several 100 ° C. occur between the individual operating states, which result in different thermal expansions of the components among one another in the case of the various components and with materials and material thicknesses used.
Im Falle der Ausdehnung ändern sich auch die Spaltmaße zwischen den einzelnen Bauteilen, sodass ein unerwünschter Blow-by-Effekt innerhalb des Turboladers auftreten kann, der wiederum den Wirkungsgrad herabsetzt. Ebenfalls kann es dazu kommen, dass die Bauteile durch unterschiedliche Ausdehnungen miteinander in Kontakt kommen, schlimmstenfalls entstehen Kollisionen der Bauteile untereinander, die wiederum Schäden oder aber einen totalen Ausfall des Turboladers mit sich bringen.In the case of expansion, the gap dimensions between the individual components change, so that an undesirable blow-by effect can occur within the turbocharger, which in turn reduces the efficiency. It can also happen that the components come into contact with each other by different expansions, in the worst case, collisions of the components with each other, which in turn bring damage or a total failure of the turbocharger with it.
Weiterhin ist die Gewichtsreduzierung bei im Kraftfahrzeugbau eingesetzten Materialien und Komponenten von besonderer Bedeutung. Hierbei steht die Herstellung eines Turboladers, insbesondere eines Turboladergehäuses in Blechbauweise unter dem Aspekt einer Möglichkeit, einen Abgasturbolader besonders gewichtsoptimiert herzustellen.Furthermore, the weight reduction in materials and components used in the automotive industry is of particular importance. Here is the production of a turbocharger, in particular a turbocharger housing in sheet metal construction under the aspect of a way to produce an exhaust gas turbocharger particularly weight optimized.
Beispielsweise ist aus der
In der Regel liegen die Innengehäuse an den Lagerflanschen an oder sind zusätzlich mit diesen stoffschlüssig gekoppelt. Hier kann es jedoch im Falle des Anliegens über die verschiedenen thermischen Ausdehnungskoeffizienten zu Undichtigkeiten und somit zu einem Blow-by kommen. Im Falle einer stoffschlüssigen Koppelung ist die Wärmeeinflusszone des thermischen Gefügevorganges geometrisch und werkstofftechnisch durch den thermischen Fügevorgang geschwächt. An dieser Stelle kann es unter extremen Belastungen oder aber über die Betriebsdauer eines Turboladers zu Rissbildung und somit auch zu Ermüdungsbrüchen oder Undichtigkeiten kommen.As a rule, the inner housings abut against the bearing flanges or are additionally cohesively coupled thereto. However, in the case of the Concerning the various thermal expansion coefficients to leaks and thus come to a blow-by. In the case of a cohesive coupling, the heat-affected zone of the thermal structural process is weakened geometrically and material-technically by the thermal joining process. At this point, under extreme loads or over the service life of a turbocharger cracking and thus fatigue fractures or leaks can occur.
Aufgabe der vorliegenden Erfindung ist es daher, die Dichtigkeit und die Dauerhaltbarkeit eines Abgasturboladers derart zu erhöhen, dass thermische Belastungen nicht zu einem frühen Bauteilversagen führen und das thermisch bedingte Ausdehnungen durch den Aufbau des Abgasturboladers kompensiert werden.Object of the present invention is therefore to increase the tightness and durability of an exhaust gas turbocharger such that thermal stresses do not lead to an early component failure and the thermally induced expansions are compensated by the structure of the exhaust gas turbocharger.
Die zuvor genannte Aufgabe wird mit den Merkmalen gemäß Patentanspruch 1 gelöst.The aforementioned object is achieved with the features according to claim 1.
Vorteilhafte Ausführungsvarianten der vorliegenden Erfindung sind Bestandteil der abhängigen Patentansprüche.Advantageous embodiments of the present invention are part of the dependent claims.
Bei einem Abgasturbolader ist das Turbinengehäuse aus einem Außengehäuse und einem Innengehäuse aufgebaut, wobei das Innengehäuse mit einem rohrförmigen Stutzen zur Anbindung eines Lagergehäuses eines Turbinenrades gekoppelt ist, wobei das Innengehäuse und der Stutzen formschlüssig miteinander gekoppelt sind. Der Abgasturbolader ist erfindungsgemäß dadurch gekennzeichnet, dass das Innengehäuse den Stutzen durchgreift und an einem Flanschkragen des Stutzens radial nach außen umgebördelt ist, wobei an dem umgebördelten Ende ein Pressring zur zusätzlichen Lagefixierung angeordnet ist.In an exhaust gas turbocharger, the turbine housing is constructed from an outer housing and an inner housing, wherein the inner housing is coupled to a tubular connecting piece for connecting a bearing housing of a turbine wheel, wherein the inner housing and the nozzle are positively coupled with each other. The exhaust gas turbocharger is inventively characterized in that the inner housing passes through the nozzle and is flanged radially on a flange collar of the neck to the outside, wherein at the flanged end a press ring for additional positional fixing is arranged.
Durch den Pressring wird das Rückfedern des Blechmaterials, welches umgebördelt wurde, verhindert. Hierdurch wird bereits während des Herstellungsprozesses ein optimaler Sitz zwischen Stutzen und Innengehäuse ermöglicht. Weiterhin wird durch die verschiedenen thermischen Ausdehnungen von Innengehäuse und Stutzen, welche durch die verschiedenen Materialstärken und auch gegebenenfalls durch die verschiedenen Werkstoffe hervorgerufen wird, ein relatives Verrutschen durch den Pressring verhindert. Weiterhin wird eine reibschlüssige Verbindung zwischen dem umgebördelten Ende sowie dem Flanschkragen durch den Pressring hergestellt. Der Pressring erhöht somit die Druckdichtigkeit. Ein Blow-by-Effekt wird dadurch weitestgehend vermieden.The press ring prevents the springback of the sheet metal material which has been flanged over. As a result, an optimal fit between the nozzle and the inner housing already during the manufacturing process allows. Furthermore, due to the different thermal expansions of the inner housing and the connecting piece, which is caused by the different material thicknesses and possibly also by the different materials, a relative slipping through the press ring is prevented. Furthermore, a frictional connection between the flanged end and the flange collar is produced by the press ring. The pressing ring thus increases the pressure tightness. A blow-by effect is thereby largely avoided.
In einer bevorzugten Ausführungsvariante der vorliegenden Erfindung wird das umgebördelte Ende des Innengehäuses im Querschnitt C-förmig umgebördelt ausgebildet. Hierdurch wird in einem bogenförmigen Verlauf über eine Fläche mit einem Radius von circa 180° eine vollflächige Anlage hergestellt, was sich positiv auf die Druckdichtigkeit auswirkt. Weiterhin wird durch die im Querschnitt C-förmig konturierte Umbördelung in axialer und radialer Richtung eine formschlüssige Koppelung ergestellt. Diese dient insbesondere der Kompensation der thermischen Ausdehnung des Innengehäuses gegenüber dem Stutzen. Ein weiterer Vorteil der C-förmigen Konfiguration der Umbördelung ist das Prinzip der Kragenumstellung. Hierdurch werden Spannungsspitzen vermieden, was wiederum Rissbildungen und/oder Brüchen vorbeugt. Ebenfalls wirkt sich die C-förmig konturierte Umbördelung auf die Relativbeweglichkeit der Bauteile zueinander aus. Hierdurch wird beispielsweise bei Temperaturwechselbelastungen ein maginales Spiel zwischen Stutzen und Innengehäuse ermöglicht, wohingegen durch den Pressring an dem umgebördelten Ende stets ein fester und druckdichter Sitz sichergestellt ist.In a preferred embodiment of the present invention, the flanged end of the inner housing is formed flanged in cross-section C-shaped. As a result, a full-surface system is produced in an arcuate course over an area with a radius of approximately 180 °, which has a positive effect on the pressure tightness. Furthermore, a form-fitting coupling is established in the axial direction and in the radial direction by the beading contoured in cross-section C-shaped. This is used in particular to compensate for the thermal expansion of the inner housing relative to the nozzle. Another advantage of the C-shaped configuration of the flanging is the principle of collar conversion. As a result, voltage spikes are avoided, which in turn prevents cracking and / or fractures. Likewise, the C-shaped contoured flange affects the relative mobility of the components to each other. As a result, a magical clearance between the nozzle and the inner housing is made possible, for example, during thermal cycling loads, whereas always a firm and pressure-tight fit is ensured by the press ring at the flanged end.
In einer weiteren vorteilhaften Ausführungsvariante ist der Flanschkragen in radialer Richtung der urbinenraddrehachse zeigend wulstartig ausgebildet. Im Zusammenspiel mit dem Innengehäuse kann somit in axialer Richtung aufgrund der geometrischen Ausbildung des Innengehäuses eine Kompensierung der thermischen Ausdehnung durch das Innengehäuse selber und in radialer Richtung eine Kompensation der unterschiedlichen thermischen Ausdehnungen durch das C-förmig, um den wulstartig ausgebildeten Flanschkragen umgebördelte Ende, sichergestellt werden. Der Flanschkragen ist dazu bevorzugt auf dem Flanschstutzen umlaufend auf die Turbinenraddrehachse zuzeigend ausgebildet.In a further advantageous embodiment variant, the flange collar is designed bead-like in the radial direction of the turbine wheel axis of rotation. In cooperation with the inner housing can thus compensate in the axial direction due to the geometrical design of the inner housing, a compensation of the thermal expansion by the inner housing itself and in the radial direction, a compensation of the different thermal Expansions by the C-shaped, around the bead-shaped flange collar flared end, be ensured. For this purpose, the flange collar is preferably designed to be circumferentially facing the turbine wheel axis of rotation on the flange socket.
In einer weiteren bevorzugten Ausführungsvariante der vorliegenden Erfindung liegt das Innengehäuse in radialer Richtung, zumindest abschnittsweise, an dem Stutzen an. Das Innengehäuse ist relativ zu dem Stutzen selber nur aus sehr dünnem Werkstoff ausgebildet. In der Folge dehnt es sich, da es zudem auch direkten Kontakt mit dem heißen Abgas hat, schneller aus. Durch die radiale Anlage an dem Stutzen wird das Innengehäuse durch den Stutzen in Folge der thermischen Ausdehnung durch Formschluss gestützt.In a further preferred embodiment of the present invention, the inner housing is in the radial direction, at least in sections, on the neck. The inner housing is formed relative to the nozzle itself only from very thin material. As a result, since it also has direct contact with the hot exhaust gas, it expands faster. Due to the radial contact with the nozzle, the inner housing is supported by the nozzle due to the thermal expansion by positive locking.
Weiterhin bevorzugt zeigt das umgebördelte Ende des Innengehäuses in axialer Richtung der urbinenraddrehachse vom Turbinengehäuse weg. Weiterhin besonders bevorzugt zeigt das umgebördelte Ende auch in radialer Richtung der Turbinenraddrehachse von dieser weg. Hierdurch wird sichergestellt, dass die Strömung des durch den Turbolader strömenden Abgases und/oder Frischgases niemals direkt auf den zwischen dem umgebördelten Ende und dem Stutzen ausgebildeten Spalt strömt. Die Druckdichtigkeit wird hierdurch weiter erhöht.Furthermore, the flanged end of the inner housing preferably points away from the turbine housing in the axial direction of the turbine wheel axis of rotation. Furthermore, particularly preferably, the flanged end also points away from the turbine wheel axis in the radial direction. This ensures that the flow of the exhaust gas flowing through the turbocharger and / or fresh gas never flows directly onto the gap formed between the flanged end and the neck. The pressure tightness is thereby further increased.
In einer weiteren bevorzugten Ausführungsvariante der vorliegenden Erfindung wird der Pressring an dem umgebördelten Ende und/oder einer Innenfläche des Stutzens zur Anlage kommend, angeordnet. Vorzugsweise erfolgt die Anordnung dabei formschlüssig und reibschlüssig. Im Falle dass der Pressring an einer Innenfläche des Stutzens sowie an dem umgebördelten Ende zur Anlage kommt, erfolgt eine weitere Abdichtung des zwischen umgebördelte Ende und Stutzen entstehenden Spaltes.In a further preferred embodiment variant of the present invention, the pressing ring is arranged at the flanged end and / or an inner surface of the connecting piece. Preferably, the arrangement takes place positively and frictionally. In the event that the press ring comes to rest on an inner surface of the nozzle and on the flanged end, there is a further sealing of the resulting between flanged end and nozzle gap.
Zur Erhöhung der Druckdichtigkeit und der Festigkeit der Verbindung ist zwischen dem Pressring und dem umgebördelten Ende weiterhin ein Lotspalt ausgebildet, vorzugsweise ist in dem Lotspalt eine stoffschlüssige Verbindung, insbesondere eine Lotverbindung, ausgebildet. Die Lotverbindung beugt einer Verdrehung während der Herstellung und/oder Bearbeitung des erfindungsgemäßen Turboladergehäuses entgegen. Weiterhin wird durch die Lotverbindung die Wärmeleitung zwischen den einzelnen Bauteilen, also von Pressring über Innengehäuse zu Stutzen, gefördert. In der Folge reduziert sich die Bauteilbelastung an kritischen Punkten durch lokale Erwärmung bzw. Überhitzung.To increase the pressure tightness and the strength of the connection, a solder gap is further formed between the press ring and the flanged end, preferably in the solder gap a cohesive connection, in particular a solder joint is formed. The solder joint bows one Distortion during the manufacture and / or processing of the turbocharger housing according to the invention. Furthermore, the heat conduction between the individual components, that is from press ring via inner housing to neck, promoted by the solder joint. As a result, the component load at critical points is reduced by local heating or overheating.
In einer weiteren vorteilhaften Ausführungsvariante der vorliegenden Erfindung wird zwischen dem Pressring und der Innenfläche des Flansches eine zusätzliche formschlüssige Verbindung der sich jeweils berührenden Oberflächen ausgebildet, vorzugsweise handelt es sich dabei um eine Verzahnung, insbesondere eine Mikroverzahnung der Oberflächen. Beispielsweise kann diese Verzahnung durch eine Anrauhung beider Oberflächen oder aber auch nur einer Oberfläche erfolgen. Eine Verdrehung des Innengehäuses zu dem Flanschkragen wird durch die Verzahnung verhindert.In a further advantageous embodiment of the present invention, an additional form-fitting connection of the respectively touching surfaces is formed between the pressing ring and the inner surface of the flange, preferably a toothing, in particular a micro-toothing of the surfaces. For example, this toothing can be done by a roughening of both surfaces or else only one surface. A rotation of the inner housing to the flange collar is prevented by the toothing.
In einer weiteren vorteilhaften Ausführungsvariante der vorliegenden Erfindung wird zwischen dem Flanschkragen und dem um den Flanschkragen umgebördelten Ende des Innengehäuses eine zusätzliche formschlüssige Verbindung der sich berührenden Oberflächen ausgebildet, vorzugsweise eine Verzahnung und/oder zwischen einer Turbinenseite des Stutzens und dem dort zumindest abschnittsweise anliegenden Innengehäuse eine zusätzliche formschlüssige Verbindung der sich berührenden Oberflächen, vorzugsweise eine Verzahnung, insbesondere eine Mikroverzahnung ausgebildet. Auch hier wird während des Herstellungsprozesses und/oder während des Betriebs des erfindungsgemäßen Turboladers ein Verdrehen und/oder Verrutschen, insbesondere im Koppelungsbereich, verhindert.In a further advantageous embodiment variant of the present invention, an additional form-fitting connection of the contacting surfaces is formed between the flange collar and the end of the inner casing flanged around the flange collar, preferably a toothing and / or between a turbine side of the nozzle and the inner housing at least partially abutting thereon additional positive connection of the contacting surfaces, preferably a toothing, in particular a micro-toothing formed. Again, during the manufacturing process and / or during operation of the turbocharger according to the invention, a twisting and / or slipping, in particular in the coupling region, prevented.
Bei den Verzahnungen handelt es sich vorzugsweise weiterhin um axial und/oder radial orientierte Verzahnungen. Hierbei ist eine Ausrichtung der Zahnstruktur unter der Richtungsangabe zu verstehen.The toothings are preferably furthermore axially and / or radially oriented toothings. Here, an orientation of the tooth structure is to be understood by the directional indication.
In einer weiteren bevorzugten Ausführungsvariante der vorliegenden Erfindung ist die Verzahnung zusätzlich verlötet.In a further preferred embodiment of the present invention, the toothing is additionally soldered.
In einer bevorzugten Ausführungsvariante wird der Pressring aus Edelstahl hergestellt. Bevorzugt wird eine Stahllegierung zur Herstellung des Pressrings verwendet, welche nachfolgend aufgelistete chemische Bestandteile, ausgedrückt in Gew.-% aufweist:
Bevorzugt weist die eingesetzte Edelstahllegierung eine Streckgrenze RP 0,2 von 230 N/mm2 auf. Die Zugfestigkeit beträgt besonders bevorzugt 550 N/mm2 bis 750 N/mm2.Preferably, the stainless steel alloy used has a yield strength RP 0.2 of 230 N / mm 2 . The tensile strength is more preferably 550 N / mm 2 to 750 N / mm 2 .
Im Rahmen der Erfindung ist es hier jedoch auch möglich, ein Stahl der Werkstoffnummer 1.4541 (X6CrNiTi18-10), oder der Werkstoffnummer 1.4571 (X6CrNiMoTi17-12-2) einzusetzen. Bei Abgastemperaturen von >900° C, wie sie bei Ottomotoren auftreten, können z.B. auch Werkstoffe mit den Werkstoffnummem 1.4841, 1.4845, 1.4876, 2.4851 und 2.4856 verwendet werden. Bei geringer zu erwartenden Abgastemperaturen (<900° C), beispielsweise bei einem Dieselverbrennungsmotor, ist es auch möglich, einen Werkstoff mit der Werkstoffnummer 1.4509 (X2CrTiNb18) oder aber einen Werkstoff mit der Werkstoffnummer 1.4512 (X2CrTi12) einzusetzen. Ebenso eignen sich Werkstoffe mit den Werkstoffnummern 1.4521 oder 1.4511.In the context of the invention, however, it is also possible here to use a steel of the material number 1.4541 (X6CrNiTi18-10), or the material number 1.4571 (X6CrNiMoTi17-12-2). At exhaust gas temperatures of> 900 ° C, such as occur in gasoline engines, materials with the material numbers 1.4841, 1.4845, 1.4876, 2.4851 and 2.4856 can also be used. At low expected exhaust gas temperatures (<900 ° C), for example, in a diesel internal combustion engine, it is also possible, a material with the material number 1.4509 (X2CrTiNb18) or a Use material with the material number 1.4512 (X2CrTi12). Also suitable are materials with the material numbers 1.4521 or 1.4511.
Wichtig ist im Rahmen der Erfindung, dass sowohl der Werkstoff des Flansches, als auch der Werkstoff des Pressringes gleich sind, sodass ein gleiches Ausdehnungsverhalten erzeugt wird, was sich besonders vorteilig auf die hergestellte Abdichtung auswirkt.It is important in the context of the invention that both the material of the flange, as well as the material of the press ring are the same, so that an equal expansion behavior is generated, which has a particularly advantageous effect on the seal produced.
Weitere Vorteile, Merkmale, Eigenschaften und Aspekte der vorliegenden Erfindung sind Bestandteil der folgenden Beschreibung. Bevorzugte Ausführungsvarianten werden in der schematischen Figur dargestellt. Diese dient dem einfachen Verständnis der Erfindung.Further advantages, features, characteristics and aspects of the present invention are part of the following description. Preferred embodiments are shown in the schematic figure. This is for easy understanding of the invention.
In der Figur werden für gleiche oder ähnliche Bauteile dieselben Bezugszeichen verwendet, auch wenn eine wiederholte Beschreibung aus Vereinfachungsgründen entfällt.In the figure, the same reference numerals are used for the same or similar components, even if a repeated description is omitted for reasons of simplicity.
Die Figur zeigt ein erfindungsgemäßes Turbinengehäuse 1 eines Abgasturboladers 2, aufweisend ein Innengehäuse 3 und ein Außengehäuse 4. Das Innengehäuse 3 ist mit einem Stutzen 5 zur Anbindung an ein hier nicht näher dargestelltes Lagergehäuse gekoppelt. Im Koppelungsbereich 6 weist der Stutzen 5 einen Flanschkragen 7 auf, der wulstartig in radialer Richtung R auf die Turbinenraddrehachse 8 zeigend ausgebildet ist.The figure shows an inventive turbine housing 1 of an exhaust gas turbocharger 2, comprising an inner housing 3 and an outer housing 4. The inner housing 3 is coupled to a connecting piece 5 for connection to a bearing housing not shown in detail here. In the coupling region 6, the nozzle 5 has a flange collar 7, which is formed like a bead in the radial direction R pointing to the turbine wheel axis 8.
Der Flanschkragen 7 wird von dem Innengehäuse 3 in axialer Richtung A der Turbinenraddrehachse 8 im Koppelungsbereich durchgriffen und ist an einem Ende 9 um den Flanschkragen 7 umgebördelt. Die Umbördelung ist im Querschnitt im Wesentlichen C-förmig 10 konfiguriert. Zur Erhöhung des durch die Bördelung hergestellten Presssitzes ist ein Pressring 11 an dem umgebördelten Ende 9 derart angeordnet, dass es zu einer form- und kraftschlüssigen Koppelung 12 mit einer Außenseite des umgebördelten Endes 9 sowie einer Innenfläche 14 des Stutzens 5 zur Anlage kommt.The flange collar 7 is penetrated by the inner housing 3 in the axial direction A of the turbine wheel axis 8 in the coupling region and is flanged around the flange collar 7 at one end 9. The bead is configured in cross-section substantially C-shaped 10. To increase the press fit produced by the flange, a
Zwischen der Innenfläche 14 des Stutzens 5 und dem Pressring 11 und/oder zwischen dem umgebördelten Ende 9 und dem Flanschkragen 7 und/oder zwischen dem Innengehäuse 3 und dem Stutzen 5 in einem radialen Anlagebereich 15 können erfindungsgemäß Mikroverzahnungen 16 ausgebildet sein. Zwischen dem Pressring 11 selber und der Außenseite 13 des umgebördelten Endes 9 ist erfindungsgemäß optional ein Lotspalt mit einer darin befindlichen Lotverbindung 17 ausgebildet.Between the
- 1 -1 -
- Turbinengehäuseturbine housing
- 2 -2 -
- Abgasturboladerturbocharger
- 3 -3 -
- Innengehäuseinner housing
- 4 -4 -
- Außengehäuseouter casing
- 5 -5 -
- StutzenSupport
- 6 -6 -
- Koppelungsbereichcoupling area
- 7 -7 -
- Flanschkragenflange collar
- 8 -8th -
- TurbinenraddrehachseTurbinenraddrehachse
- 9 -9 -
- EndeThe End
- 10 -10 -
- C-förmigC-shaped
- 11 -11 -
- Pressringpress ring
- 12 -12 -
- form- und kraftschlüssige Koppelungpositive and non-positive coupling
- 13 -13 -
- Außenseite zu 9Outside to 9
- 14 -14 -
- Innenflächepalm
- 15 -15 -
- radialer Anlagebereichradial contact area
- 16 -16 -
- Mikroverzahnungmicrotoothing
- 17 -17 -
- Lotspalt mit LotverbindungLotspalt with solder connection
- R -R -
- Radialrichtungradial direction
- A -A -
- Axialrichtungaxially
Claims (10)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102011050506A DE102011050506B4 (en) | 2011-05-19 | 2011-05-19 | turbocharger |
Publications (3)
Publication Number | Publication Date |
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EP2525050A2 true EP2525050A2 (en) | 2012-11-21 |
EP2525050A3 EP2525050A3 (en) | 2017-10-04 |
EP2525050B1 EP2525050B1 (en) | 2018-06-20 |
Family
ID=45932162
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP12160695.8A Active EP2525050B1 (en) | 2011-05-19 | 2012-03-22 | Exhaust gas turbocharger |
Country Status (4)
Country | Link |
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US (1) | US9097181B2 (en) |
EP (1) | EP2525050B1 (en) |
JP (1) | JP5384692B2 (en) |
DE (1) | DE102011050506B4 (en) |
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WO2015185408A1 (en) * | 2014-06-02 | 2015-12-10 | Mitsubishi Turbocharger And Engine Europe B.V. | A spiral turbine casing of a turbocharger |
WO2016055444A1 (en) * | 2014-10-08 | 2016-04-14 | Ksb Aktiengesellschaft | Centrifugal pump |
EP3045687A1 (en) * | 2015-01-14 | 2016-07-20 | Benteler Automobiltechnik GmbH | Turbine housing for an exhaust gas turbocharger |
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DE112011105790B8 (en) * | 2011-11-02 | 2017-08-17 | Toyota Jidosha Kabushiki Kaisha | Turbine housing and exhaust gas turbocharger |
DE102012009090A1 (en) | 2012-05-09 | 2013-11-14 | Benteler Automobiltechnik Gmbh | Connection of a double-walled turbocharger housing |
DE102013109446B4 (en) | 2013-08-30 | 2015-11-26 | Benteler Automobiltechnik Gmbh | Exhaust manifold with insulation sleeve |
DE102013111561A1 (en) * | 2013-10-21 | 2015-04-23 | Ihi Charging Systems International Gmbh | turbocharger |
DE102014102038B4 (en) | 2014-02-18 | 2016-11-24 | Benteler Automobiltechnik Gmbh | Exhaust system component and method for connecting a first pipe component and a second pipe component of an exhaust system component |
DE102014103809A1 (en) | 2014-03-20 | 2015-12-03 | Benteler Automobiltechnik Gmbh | Exhaust manifold for an exhaust system of an internal combustion engine |
DE102014105656B4 (en) | 2014-04-22 | 2017-02-02 | Benteler Automobiltechnik Gmbh | exhaust manifold |
US10544703B2 (en) | 2017-01-30 | 2020-01-28 | Garrett Transportation I Inc. | Sheet metal turbine housing with cast core |
US10494955B2 (en) | 2017-01-30 | 2019-12-03 | Garrett Transportation I Inc. | Sheet metal turbine housing with containment dampers |
US10472988B2 (en) * | 2017-01-30 | 2019-11-12 | Garrett Transportation I Inc. | Sheet metal turbine housing and related turbocharger systems |
US10436069B2 (en) * | 2017-01-30 | 2019-10-08 | Garrett Transportation I Inc. | Sheet metal turbine housing with biaxial volute configuration |
US10690144B2 (en) | 2017-06-27 | 2020-06-23 | Garrett Transportation I Inc. | Compressor housings and fabrication methods |
US11136997B2 (en) * | 2019-07-23 | 2021-10-05 | Ford Global Technologies, Llc | Methods and systems for a compressor housing |
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- 2012-03-22 EP EP12160695.8A patent/EP2525050B1/en active Active
- 2012-04-23 JP JP2012097285A patent/JP5384692B2/en active Active
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DE10022052A1 (en) | 1999-05-26 | 2001-03-01 | Gillet Heinrich Gmbh | Turbine casing for exhaust gas turbocharger has inlet funnel, rotor casing and exhaust pipe made from embossed or deep-drawn sheet metal, and inlet funnel and exhaust pipe are welded to rotor casing which comprises two half shells |
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WO2015185408A1 (en) * | 2014-06-02 | 2015-12-10 | Mitsubishi Turbocharger And Engine Europe B.V. | A spiral turbine casing of a turbocharger |
NL1040828B1 (en) * | 2014-06-02 | 2016-05-12 | Mitsubishi Turbocharger And Engine Europe B V | A spiral turbine casing of a turbocharger. |
WO2016055444A1 (en) * | 2014-10-08 | 2016-04-14 | Ksb Aktiengesellschaft | Centrifugal pump |
EP3045687A1 (en) * | 2015-01-14 | 2016-07-20 | Benteler Automobiltechnik GmbH | Turbine housing for an exhaust gas turbocharger |
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Also Published As
Publication number | Publication date |
---|---|
DE102011050506B4 (en) | 2013-04-18 |
EP2525050B1 (en) | 2018-06-20 |
JP5384692B2 (en) | 2014-01-08 |
US20120294709A1 (en) | 2012-11-22 |
EP2525050A3 (en) | 2017-10-04 |
JP2012241715A (en) | 2012-12-10 |
DE102011050506A1 (en) | 2012-11-22 |
US9097181B2 (en) | 2015-08-04 |
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